Modular liquid propellant gun

ABSTRACT

A gun of the kind in which liquid propellant is burned in the firing chamber to fire a projectile from the gun is constructed so that a number of gun modules can be combined in a modular gun. Each gun module is cam controlled, and a common cam is used to control each gun module in the modular gun. The cam can be a flexible cam having a belt configuration to permit the gun modules to be arranged in both circular groupings and in noncircular groupings, such as side by side. The modular gun includes fixed, non-rotating gun modules to eliminate the need for tangential velocity correction factors in the fire control and the need to accelerate the mass of the barrel assembly to operational speed. The individual gun module includes propellant injection mechanism for injecting propellant at high pressure when a non-hypergolic bi-propellant is used as the propellant. One or more hydraulic actuators are used to develop the high injection pressures and to operate other components of the gun, such as the bolt. The hydraulic actuators are also engaged with the cam to interlock the actuators and the controls for the actuators through the cam. A source of pressurized hydraulic fluid independent of the gun is used to power the actuators so that the weight and profile of the gun are kept to a minimum. The hydraulic system includes a compound spool control valve which operates in a dual mode to permit normal cyclic operation of the gun during firing and to maintain the gun in an open bolt condition during armed but non-firing operations. The hydraulic system includes a misfire detection mechanism and module shutdown valve which locks a misfired gun module in the closed bolt condition without the need to depressurize the hydraulic circuits of the other gun modules and without the need to include additional bypass circuits. The injection mechanism for injecting the bi-propellant includes two pistons which are yoked together and operated by a single actuator to inject the propellant into the firing chamber both in metered amounts and in a constant mix ratio. The pistons for injecting the bi-propellant include valves in the pistons, and the pistons are drawn through the fuel on retraction strokes of the pistons. The injection mechanism is retracted away from the firing chamber after the firing of a burst to isolate the propellant in the injection mechanism from the heat of the firing chamber. A rotary lock is mounted closely adjacent the bolt mechanism and engages a relieved area of the bolt in the locked position of the lock so that a quite small force on the lock will hold the bolt mechanism locked against high combustion chamber pressures tending to open the bolt.

United States Patent [1 1 Broxholm et a1.

[ Nov. 18, 1975 1 MODULAR LIQUID PROPELLANT GUN [75] Inventors: Thomas M. Broxholm, Palo Alto; Lester C. Elmore, Portola Valley, both of Calif.

[73] Assignee: Pulsepower Systems, Inc., San Carlos, Calif.

[22] Filed: Jan. 14, 1974 [21] Appl. No.: 433,375

Related US. Application Data [62] Division of Ser, No. 104,610, Jan. 7, 1971, Pat. No.

[52] US. Cl. 91/37; 91/36; 91/413; 91/461; 91/471 [51] Int. Cl. F15B 21/02 [58] Field of Search 91/382, 413, 461, 304,

91/507, 35, 37, 39, 36, 471; 89/7, 41 H, 43 R; 74/57, 471 R [56] References Cited UNITED STATES PATENTS 1,195,665 8/1916 Etter 74/57 2,434,538 1/1948 Baston 1 1 91/37 X 2,610,614 9/1952 Sedgwick 91/382 2,818,881 l/l958 Bonner et a1. 91/36 X 3,354,789 1 H1967 Schenkelberger 91/413 3,585,669 6/1971 Moret et a1. 91/31 X 3,763,739 10/1973 Tassie 1 89/7 3,802,320 4/1974 Stafford 91/413 X Primary Examiner-Carlton R. Croyle Assistant ExaminerEdward Look Attorney, Agent, or Firm-Owen, Wickersham & Erickson [57] ABSTRACT flexible cam having a belt configuration to permit the gun modules to be arranged in both circular groupings 223 ll! l 191 a /235 and in non-circular groupings, such as side by side. The modular gun includes fixed, non-rotating gun modules to eliminate the need for tangential velocity correction factors in the fire control and the need to accelerate the mass of the barrel assembly to operational speed. The individual gun module includes propellant injection mechanism for injecting propellant at high pressure when a non-hypergolic bi-propellant is used as the propellant. One or more hydraulic actuators are used to develop the high injection pressures and to operate other components of the gun, such as the bolt. The hydraulic actuators are also engaged with the cam to interlock the actuators and the controls for the actuators through the cam. A source of pressurized hydraulic fluid independent of the gun is used to power the actuators so that the weight and profile of the gun are kept to a minimum. The hydraulic system includes a compound spool control valve which operates in a dual mode to permit normal cyclic operation of the gun during firing and to maintain the gun in an open bolt condition during armed but nonfiring operations. The hydraulic system includes a misfire detection mechanism and module shutdown valve which locks a misfired gun module in the closed bolt condition without the need to depressurize the hydraulic circuits of the other gun modules and without the need to include additional bypass circuits. The injection mechanism for injecting the bi-propellant includes two pistons which are yoked together and operated by a single actuator to inject the propellant into the firing chamber both in metered amounts and in a constant mix ratio. The pistons for injecting the bipropellant include valves in the pistons, and the pistons are drawn through the fuel on retraction strokes of the pistons. The injection mechanism is retracted away from the firing chamber after the firing of a burst to isolate the propellant in the injection mechanism from the heat of the firing chamber. A rotary lock is mounted closely adjacent the bolt mechanism and engages a relieved area of the bolt in the locked position of the lock so that a quite small force on the lock will hold the bolt mechanism locked against high combustion chamber pressures tending to open the bolt.

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U.S., Patent Nov. 18,1975 Sheet2of13 3,919,922

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U.S., Patent Nov. 18, 1975 Sheet70f13 3,919,922

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US. Patent Nov. 18, 1975 Sheet 8 of 13 3,919,922

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U.S. Patent Nov. 18, 1975 Sheet 10 of 13 3,919,922

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US. Patent Nov. 18, 1975 Sheetl10f13 3,919,922

US. Patent Nov. 18, 1975 Sheet 13 0 MODULAR LIQUID PROPELLANT GUN This application is a division of parent application Ser. No. 104,610 filed Jan. 7, 1971 and entitled Modular Liquid Propellant Gun and claims the benefit of the filing date of the parent application.

This invention relates to a gun of the kind in which liquid propellant is burned in the firing chamber to fire the projectile from the gun.

This invention relates particularly to a liquid propellant gun constructed as an individual gun module so that a number of gun modules can be combined in a modular gun.

In conventional guns powder for firing each projectile is carried in a case attached to the projectile.

A liquid propellant gun has a number of advantages over such conventional guns.

If the liquid propellant gun uses the same size projectile as a conventional gun, the projectile feed for the liquid propellant gun can be simplified and can be made considerably lighter in weight than for a conventional gun. Or, a considerably larger charge can be used for higher performance without having to increase the size of the projectile feed mechanism.

A liquid propellant gun can produce a flatter combustion chamber pressure-time characteristic than a solid propellant gun. Hence performance equivalent to a solid propellant gun can be obtained at lower pressure.

High cyclic rates of fire are possible with a liquid propellant gun.

Because the propellant is a liquid the propellant can be easily pumped to the firing chamber from a storage area remote from the gun itself. This permits flexibility of installation.

When the gun is installed in an aircraft and a nonhypergolic bi-propellant is used, one of the components of the non-hypergolic bi-propellant can be the fuel used for the engine of the aircraft.

The liquid propellant gun permits a low profile, clean exterior design so that an individual liquid propellant gun module, or a modular grouping of liquid propellant gun modules, can be installed in locations that would not accommodate a conventional gun.

It is a primary object of the present invention to incorporate these inherent advantages of a liquid propellant gun in a modular gun.

Further objects of the present invention include the specific structures and features of operation noted in the abstract above.

Other and further objects of the present invention will be apparent from the following description and in the art without departing from the present invention and the purview of the appended claims.

IN THE DRAWINGS:

FIG. 1 is an isometric exploded view (partially broken away to show details of construction) of an individual gun module constructed in accordance with one embodiment of the present invention. FIG. 1 shows the 2 three main components of an individual gun module-the barrel assembly. the receiver assembly, and the control assembly;

FIG. 2A and FIG. 2B are a plan view (partly broken away along the line and in the direction indicated by the arrows 2-2 in FIG. 11) of the gun shown in FIG. 1; FIG. 3A and FIG. 3B are a side elevation view in cross section of the gun module shown in FIG. 1;

FIG. 4 is a fragmentary plan view taken generally along the line and in the direction indicated by the arrows 4-4 in FIG. 9;

FIG. 5 is a fragmentary top plan view taken generally along the line and in the direction indicated by the arrows 5-5 in FIG. 3B;

FIG. 6 is an elevation view taken along the line and in the direction indicated by the arrows 6-6 in FIG. 3A;

FIG. 7 is an elevation view taken along the line and in the direction indicated by the arrows 77 in FIG. 38;

FIG. 8 is an elevation view taken along the line and in the direction indicated by the arrows 88 in FIG. 3B;

FIG. 9 is an elevation view taken along the line and in the direction indicated by the arrows 9-9 in FIG. 38;

FIG. 10 is an elevation view taken along the line and in the direction indicated by the arrows 10-10 in FIG. 313;

FIG. 11 is an elevation view taken along the line and in the direction indicated by the arrows 11-11 in FIG. 3B;

FIG. 12 is an elevation view taken along the line and in the direction indicated by the arrows 12-12 in FIG 3A. FIG. 12 illustrates how four individual gun modules can be arranged in a circular grouping in a modular gun constructed in accordance with an embodiment of the present invention;

FIG. 13 is a schematic front end elevation view illustrating the way in which the projectiles are spaced at one half the pitch between adjacent gun modules. FIG. 13 illustrates how four individual gun modules may be arranged side by side in a modular gun constructed in accordance with an embodiment of the present invention;

'FIG. 14A and FIG. 14B are a schematic diagram of a hydraulic drive control system for a single gun module as shown in FIG. 1;

FIG. 15 is a top plan view of a cam having a hollow cylindrical configuration for use with four gun modules arranged in a circular grouping as best illustrated in FIG. 12. Parts of FIG. 15 have been broken away to show the cam faces on the interior surface of the hollow cylindrical cam;

FIG. 16 is an end view of the cam shown in FIG. 15 and is taken along the line and in the direction indicated by the arrows 16-16 in FIG. 15;

FIG. 17 is a fragmentary cross sectional view like FIG. 3A showing a modification of the fuel injection mechanism for the gun module shown in FIG. 1. FIG. 17A illustrates how the propellant injection mechanism is retracted away from the firing chamber after the firing of a burst;

FIG. 18 is an inside developed view of the inside surface of the hollow cylindrical cam shown in FIG. 15;

FIG. 19 is a fragmentary cross section view taken along the line and in the direction indicated by the arrows 19-19 in FIG. 18;

FIG. 20 is a pictorial view of one embodiment of a bolt locking mechanism for the gun module shown in FIG. 1. FIG. 20 shows the bolt locking mechanism in the unlocked mode;

FIG. 21 is a view like FIG. showing the lock mechanism in the locked mode;

FIG. 22 is a view like FIG. 21 but with parts partially broken away to show details of construction;

FIGS. 23 and 24 are side elevation views of the lock mechanism of FIGS. 20-21 showing the bolt and lock in the unlocked position in FIG. 23 and in the locked position in FIG. 24;

FIGS. 25 and 26 are views like FIGS. 23 and 24 of another embodiment of a lock mechanism constructed in accordance with the present invention;

FIGS. 27 and 28 are views like FIGS. 23 and 24 of still another embodiment of the lock mechanism constructed in accordance with the present invention; and

FIG. 29 is a pictorial view of the bolt and actuator sub-assembly.

An individual gun module constructed in accordance with one embodiment of the present invention is indicated generally by the reference numeral 31 in FIG. 1.

The gun module 31 includes three main components-a barrel assembly 33, a receiver assembly 35, and a control assembly 37.

The gun module 31 may be used by itself or (as will be described in greater detail below) may be arranged in both circular groupings (as shown in FIG. 12) or in non-circular groupings (as shown in FIG. 13) to form modular guns. The modular guns are indicated generally by reference numerals 39 and 41 in FIGS. 12 and 13.

The gun module 31 is a liquid propellant gun. The gun burns a liquid propellant in the firing chamber to propel the projectile.

The particular embodiment of the gun 31 shown in the drawings and described below is constructed to use a bi-propellant, a propellant having two components which are mixed in the firing chamber. The gun module 31 shown in FIG. 1 uses a non-hypergolic bi-propellant. The two components of the bi-propellant do not ignite on contact.

Non-hypergolic bi-propellants have this advantage over hypergolic bi-propellants. The non-hypergolic bipropellant can be handled in the same way as a monopropellant. For example, the firing chamber can be fired, without spontaneous ignition, as in a mono-propellant. Because of this fact, the chamber can be tired without having to pump against combustion pressure; and the propellant can be loaded in an exact amount before ignition is started. It should be noted, however, that many of the principles of the present invention could be applied to liquid propellant guns using hypergolic bi-propellants. Most of the principles of the present invention can be applied to liquid propellant guns using mono-propellants.

The bi-propellant is ignited in the combustion chamber by a spark plug in the embodiment of the gun module shown in FIG. 1. Ignition can also be accomplished by compression ignition or by injecting a chemical into the propellant. The present invention is not restricted to spark ignition.

The gun module 31 is a cam-controlled, hydraulically powered gun. The main cam maintains a proper sequence and timing relationship between the various components of the gun while hydraulic power is the primary energy source.

The cam for controlling the gun module 31 is shown in FIGS. 15, 16, 18 and l9.

A hydraulic drive control system of the control assembly 37 is shown in schematic diagram in FIGS. 14A and 148.

The bolt and injector sub-assembly of the receiver assembly 35 is shown in FIG. 29.

Details of construction of the gun module 31 will now be described with reference primarily to FIGS. 3A and 3B and FIGS. 2A and 2B.

The barrel assembly 33 includes a barrel 43.

The receiver assembly 35 includes a receiver 45.

The receiver assembly 35 also includes an end plate 47 attached to the back end of the receiver 45 by a number of cap screws 46.

The hydraulic control assembly 37 is mounted on the receiver 45 in front of the end plate 47.

The main cam 49 is mounted for rotation between the receiver 45 and the hydraulic control assembly 37. The main cam 49 is a hollow, cylindrical member (as best shown in FIGS. 15 and 16), and the rear end of the cam 49 is mounted for rotation on a bearing 51 in the end plate 47. The front end of the cam 49 may also be mounted for rotation on a bearing (not shown in the drawings) or may rotate on the receiver 45. The cam 49 has cam traces on both the inside and the outside peripheries. As will be described in greater detail below, the cam traces on the inside peripheries engage cam followers of actuators in the receiver 45 while the cam traces on the outside periphery engage cam followers of control valves in the hydraulic control assembly 37.

The cam 49 in the embodiment shown in FIG. 12 can be a rigid member. In other applications, e.g., the FIG. 13 embodiment, the cam 49 must be a flexible member as illustrated to accommodate non-circular groupings of modules. As will become more apparent from the description to follow, a flexible cam is possible because of the low cam face loads of the present invention. The low cam face loads are possible because the cam does not drive the bolt assembly. The force for driving the bolt assembly is supplied by hydraulic actuators, and the cam serves only to maintain the proper phase relationship between the actuators and the control valves.

The cam 49 includes gear teeth 53 on the outside periphery of the cam. An electric or hydraulic motor (not shown in the drawings) drives the cam (in counterclockwise rotation as viewed in FIGS. 8-11) by means of the gear teeth 53.

The receiver 45 mounts a bolt 55 and propellant injection mechanism for reciprocation toward and away from combustion chamber 57 at the inlet end of the barrel 43.

The bolt and injector sub-assembly is best illustrated in FIG. 29. In FIG. 29 the propellant injection mechanism 59 includes a yoke 61, an acid piston 63, a fuel piston 65 and a hydraulic actuator 68. In the embodiment of the invention shown in FIGS. 2A, 2B, 3A, 3B and FIG. 29, the acid piston reciprocates within a cylinder formed in the bolt 55, and the fuel piston 65 reciprocates within a cylinder 69 formed in the bolt 55.

The acid, or oxidizer, component of the bi-propellant is injected from the cylinder 70 through a port 71 into a central bore or pre-combustion chamber 73 of the bolt 55 and then into the combustion chamber 57.

The fuel in an aircraft installation may be the same fuel (such as JP 4) used for the aircraft engine. The fuel is injected from the cylinder 69 into the pre-combustion chamber 73 and the combustion chamber 57 through a port 72 shown in FIGS. 2A.

Piston 63 includes a one-way check valve 75 at the forward end of the piston.

The piston 65 includes a one-way check valve 77 at the forward end of the piston.

These check valves permit the fuel to flow through the interior of the pistons and through the head of the piston into the cylinder 700 and the cylinder 69 during the retraction strokes of the pistons within the cylinders 70 and 69.

The strokes of the pistons 63 and 65 are the same since the pistons are yoked together by the yoke 61. The proper mix ratio for the two components of the bipropellant is obtained by the relative diameters of the pistons 67 and 65. The two components of the bi-propellant are therefore injected into the firing chamber in both metered amounts and in a constant mix ratio.

A spark plug 79 is mounted for reciprocation within the bolt 55 in a bore 81 which forms a continuation of a pre-combustion chamber 73.

The spark plug 79 closes off the propellant injection port 71 of the cylinder 70 and the port 72 for the cylinder 69 as the spark plug is moved forward during a cycle of operation to control the end of the propellant injection strokes.

As best shown in FIG. 29, the bolt is actuated by a hydraulic actuator 83 and an actuator rod 85.

The bolt 55 includes a bolt cam follower 87.

The fuel injection yoke 61 includes a cam follower 89.

The spark plug includes a spark plug cam follower 91.

With continued reference to FIG. 29, the hydraulic fluid for the propellant injection mechanism actuator 68 is brought in through a hydraulic line 93 and a hydraulic port 95.

The fuel for the fuel piston 65 is supplied through a fuel line 97.

The oxidizer for the acid piston 63 is supplied through a line 99.

The injector actuator 68 includes a piston 64 slideable in a bore 66. The piston 64 in turn has an inner bore 66A.

An injector actuator hydraulic line 96 (see FIG. 4 and FIG. 29 and also FIG. slides within the bore 66A in a trombone type arrangement as the injector yoke 61 is reciprocated back and forth by the action of the piston 64 within the bore 66.

As best shown in FIGS. 28 and 3B, the fuel piston and fuel line and the acid piston and acid line also have similar trombone type arrangements.

Thus, the fuel piston 65 has a hollow interior forming a bore 65A, and this hollow bore slides back and forth on the outside of the fuel line 97 during reciprocation of the piston 65 by the yoke 61.

The acid piston 63 has a bore 62, and this bore 62 slides back and forth on the exterior of the acid line 99 as the acid piston 63 is reciprocated by the yoke 61.

Suitable seal means, as shown in the drawings, are provided to accomplish the necessary sealing.

As best shown in FIG. 3B, the fuel line 97 is connected through the end plate 47 to a fuel port 101, and the acid line 99 is connected through the end plate 47 to an acid port 103.

FIG. 3A shows the bolt 55 at its full forward position.

A projectile 105, as shown in FIG. 3A, has been forced forward to the position illustrated by the forward movement of the bolt 55 and also by the liquid propellant injected behind the projectile 105 into the firing chamber 57 by the forward movement of the fuel piston and the acid piston 63. The projectile is forced forward by the liquid propellant injected in the chamber 57. The forward motion is stopped by the resistance produced by the forcing cone. The way in which the projectile is loaded into the receiver and forced forward by the bolt and the liquid propellant insures that the firing chamber 57 and pre-combustion chamber 73 are completely filled with liquid propellant to eliminate an ullage problem.

The projectile 105 may preferably be fed to the receiver by a linkless belt 107 as shown in FIG. 12.

As shown in FIG. 12, (and as also shown in the lower lefthand corner of FIG. 14A), a projectile loader lever 109 bats a projectile 105 out of the belt 107 and into a curved slot 111 shaped to drop the projectile 105 into the proper position in the receiver assembly 31 in front of the bolt 55.

The projectile loader lever 109 is in the form ofa bell crank (as best shown in FIG. 14A) and is pivotally connected to the receiver 45 by a pin 110.

The lever 109 is pivoted about the pin by a hydraulic actuator indicated generally by the reference numeral 112 in FIG. 14A.

The actuator 112 includes a housing 114 and a piston 116 reciprocable within a bore in the housing. A rod of the piston 116 is connected to the lever 109 in a pin joint connection 118.

As shown in FIG. 3A the projectile 105 in the receiver above the bolt 55 is positioned to be moved downward and in front of the front face of the bolt 55 by the lever 109 when the bolt 55 is retracted.

Each gun module 31 includes a misfire detection and module shutdown system. This system will be described in detail with reference to FIGS. 14A and 14B, but at the present time it should be noted that the system includes a detector mechanism indicated generally by the reference numeral 113 in FIG. 2A. The mechanism 113 includes a housing clamped to the front end of the barrel 43 by bolts and nuts as illustrated. The housing 115 has a restricted orifice 117 which fits within an opening 119 in the barrel. The orifice 117 opens into a cylinder 121 in the interior of the housing 115. A second restricted orifice 123 also communicates with the interior of the cylinder 121 and extends through the wall of the housing 115 to connect the cylinder with the ambient atmosphere.

A piston 125 is reciprocable within the cylinder 121.

A piston rod 127 extends from the rearward end of the piston 125 through an end wall of the housing 115 and through a tube 129 back to a module shutdown control valve 223 as shown in FIG. 14B and as will be described in greater detail below.

An opening 131 extends through the front end wall of the housing 115 to vent the cylinder in front of the piston 125 to ambient atmosphere to prevent lock-up.

The orifices 117 and 123 are controlled orifices. The high pressure gas behind the projectile 105 enters the chamber within the cylinder 121 behind the piston 125 through the orifice 117 as the projectile is fired out of the barrel 43. The orifices 117 and 123 permit the escape of the pressurized gas from the interior of the housing 115 at a controlled rate to provide a certain leak down time. If another projectile is not fired within this leak down time the piston rod 127 is pulled back (to the right as viewed in FIG. 2A) by hydraulic pressure exerted on a face of the control valve, as will be described in greater detail below with reference to FIG.

The detection mechanism 113 thus detects a misfire. The detection mechanism 113 remains in the position illustrated in FIG. 2A so long as the gun module continues in normal cyclic operation and does not misfire. On a misfire the piston 125 is shifted rearward (to the right as viewed in FIG. 2A).

As shown in FIGS. 2A and 3A an inlet port 133 and an outlet port 135 are connected to the top of the barrel 43 through openings in the receiver 45 for supplying fluid to the combustion chamber 57 to purge the chamber 57 in the event of a misfire.

As best shown in FIG. 6 the fluid from the inlet port 133 flows into the combustion chamber 57 through a port 139 when a valve member 141 is positioned to permit flow between the ports 133 and 139.

As best shown in FIG. 14A a companion valve 143 controls the flow of the purge fluid out of the combustion chamber 57 through a port 145 (like the port 139) and through the outlets of 135 to sump.

As shown in FIG. 14A the valve members 141 and 143 are yoked together by a yoke 147 and spring bi ased, by springs 149 and 151, to the positions illustrated in which the valve members close off the ports 139 and 145.

A hydraulic actuator 153, which includes a piston 155 spring biased by the spring 157 to the position illustrated in FIG. 14A, opens the ports 139 and 145 by moving the valve members 141 and 143 to the left as viewed in FIG. 14A when hydraulic pressure is admitted to the interior of the actuator 153 through'the conduit 159. The flow of hydraulic fluid through the conduit 159 is under the control of a three-way time control valve 161. The three-way time delay valve 161 is controlled by the misfire detection and module shutdown system, as will be described in greater detail with reference to the description of FIGS. 14A and 148.

As best shown in FIGS. -22 the gun module 31 includes a breech lock mechanism. This breech lock mechanism is indicated generally by the reference numeral 163 in FIGS. 2022.

The breech lock mechanism, as best shown in FIG. 14A, includes a lock 165 and an actuator 167.

The actuator 167 includes a piston 169 and a rod 171. The forward end of the rod 171 has gear teeth 173 which engage corresponding gear teeth 175 on the lock. The rod 171, gear teeth 173 and gear teeth 175 form a rack-and-pinion arrangement for rotating the lock 165.

The lock 165 is a cylindrical member mounted for rotation about its longitudinal axis. The rotational axis of the lock 165 extends transverse to the axis of reciprocation of the bolt 55.

The lock 165 has a cutout or relieved area 177 which permits the lock to be mounted with the rotational axis of the lock closely adjacent to the outer periphery of the bolt 55. The relieved area 177 is shaped to, in effect, let the bolt reciprocate within the lock 165 with the outer periphery of the bolt in closely adjacent relationship to the surface of the cutout 177 of the lock when the lock is in the unlocked position.

The bolt 55 has a similar cutout or relieved area 181 which provides an abuttment face when the lock 165 is rotated into the cutout or relieved area 181.

This action is best shown in FIGS. 23 and 24.

In the configuration of the parts shown in FIGS. 23 and 24 the lock 165 has an abuttment face 179. The face 179 abutts the corresponding abuttment face 181 8 of the bolt 55, which is a part of the relieved area 177 of the lock 165.

FIGS. and 26 and FIGS. 27 and 28 show modified lock and bolt arrangements in which the abuttment face 179 of the lock is not part of the relieved area 177 I of the lock.

In this instance, however, the abuttment face 179 of the lock engages a substantial part of the relieved area of the bolt in the locked position so that only a small force exerted by the actuator 167 is required to hold the bolt in the locked position.

Since the combustion pressure developed in the combustion chamber 57 is quite large, the force on the forward face of the bolt 55 during firing is also quite large. This force on the face of the bolt acts in a direction tending to open the bolt, and it is therefore important that the lock mechanism 163 be effective to hold the 1 bolt in the locked position.

As best illustrated in FIG. 22 the spark plug 79 also has a cutoutor relieved area which engages the lock 165 when the lock 165 is rotated to the locked position.

As also illustrated in FIGS. 21 and 22, the piston 63 of the propellant injection mechanism may also be formed with a locking element 185 projecting outwardly from the piston 63 for engagement with a locking face 187 of the lock 165 when the lock is rotated to the locked position.

The locking element 185 is slidable within a slot 189 of the bolt 65. The locking of the fuel injection mechanism is not as critical as the locking of the bolt 55 and the spark plug 79 because the fuel injection mechanism is not directly exposed to the combustion pressure within the combustion chamber 57.

Before going to a discussion of the control mecha nism shown in FIGS. 14A and 143, it should be noted. that FIGS. 17 and 17A illustrate a modification of propellant injection mechanism. In these figures II'BI cylinder and piston 63 are mounted for reciprocation within a bore 70A formed in the barrel 43 and in the receiver 45 rather than in the bolt 55.

The cylinder 70 has a front end portion constructed to withstand the high pressures developed during combustion in the combustion chamber 57.

Seals, such as O-ring seals 401, prevent the loss of combustion chamber pressure.

A spring biased check valve 403 is mounted in the front end portion of the cylinder 70 to permit the flow of propellant from the cylinder through the port 71 to the combustion chamber.

The piston 63 includes a one-way check valve at the forward end of the piston.

In the operation of the embodiment shown in FIGS. 17 and 17A, the cylinder 70 remains in the forward position illustrated in FIG. 17 during the firing of a burst while the piston 63 reciprocates back and forth within the cylinder 70 during the firing of each round. After the firing of a burst, the entire cylinder 70 and piston 63 assembly is retracted to the position shown in FIG. 17A to isolate the propellant from the hot barrel 43.

The present invention retracts the propellant injection mechanism away from combustion chamber 57 so that the injection mechanism and the liquid propellant within the injection mechanism are physically isolated from the hot combustion chamber to provide a thermal barrier, that is, a physical barrier to prevent heat flow from the hot combustion chamber to the propellant. This eliminates problems of heat soak which can lead to cookoff or unwanted vaporization of fuel and combustion in the gun module 31. lt is important to provide such thermal isolation after the firing of a burst. During firing the flow rates of the liquid propellant are normally high enough to provide sufficient cooling. Thus, while the FIG. 3A embodiment of the present invention discloses retraction after each individual firing, it should be recognized that it might be desirable in some instances to retract the entire injection mechanism only after the firing of a burst as in the FIGS. 17 and 17A embodiment.

ln some instances, it may be desirable to include a low conductivity thermal barrier between the barrel and the receiver to further reduce the possibility of transfer of heat to the propellant after the firing of a burst.

A schematic diagram of the hydraulic drive control system for the gun module 31 as shown in FIGS. 14A and 14B. Pressurized hydraulic fluid for driving the various actuators is brought into the system through a line 191. The motor for producing this pressurized hydraulic fluid is preferably separate from the gun itself so that the gun can be kept light in weight and small in profile.

If the gun is installed in an aircraft the source of the pressurized hydraulic fluid can be the hydraulic system of the aircraft.

One of the features of a hydraulic control system is fast response. In the present invention the first shot is made at full cyclic rate.

The hydraulic fluid is returned from the control system to the source by a line 193.

The control system includes a bias control valve indicated generally by the reference numeral 195. The bias control valve is an on-off valve and is controlled by a trigger solenoid 197. The trigger solenoid 197 is shown in the on position in FIG. 14.

The bias control valve 195 includes a housing 199 and a valve spool 201 reciprocable within a bore in the housing 199.

Pressurized fluid flows into the housing 201 through an inlet conduit 203.

Outlet conduits 205 and 207 lead from the valve housing 199 to a housing 209 forming a part of the misfire detector mechanism 113. Outlet conduits 211 and 213 extend from housing 199 downward to other conduits which are connected to ports at opposite ends of the various control valve housings. Outlet conduits 215 and 217 connect with the return conduit 193.

Lands 219 and 221 on the spool of the bias control valve control the flow through the various conduits.

The valve spool 201 includes a cam follower 220 which engages a trace 222 in the cam 49 in the armed condition of the system with the trigger solenoid in the off position. When the trigger solenoid is energized to the on position, the cam follower remains in the cam trace 222 until a cross-over path 224 permits the cam follower to shift to the trace 226. This insures that the trigger solenoid will move the valve spool 219 to the on position in the proper time sequence with the other components of the hydraulic control system.

A spring 235 acting on the backface of the land 231 biases the spool 223, and the rod 127, in a forward direction.

Pressurized fluid, conducted through the housing 209 by the conduit 207, acts on a forward face of a land 237 to bias the spool 223 in a rearward direction.

A cam follower 239 is connected to the rearward extension of the valve spool 223 and is normally engaged in a trace 241 of the cam 49. The cam trace 241 extends around the outside circumference of the cam 49 and parallel to a second cam trace 243. A path 245 connects the traces 241 and 243.

As will be described in greater detail below in the description of the operation of the gun, the cam follower 239 remains in the trace 241 so long as a misfire does not occur. The pressure developed within the bore 121 of the housing at the end of the barrel during cyclic firing is sufficient to keep the piston 125 forward, as illustrated, when the path 245 is aligned with the cam follower 239. However, if a misfire occurs, there is insufficient pressure in the chamber 121 behind the pis ton 125, and the force developed by the pressurized hydraulic fluid acting on the forward face of the land 237 shifts the valve follower 239 from the trace 241 through the path 245 and into the trace 243; and the cam follower 239 thereafter remains in the trace 243. This cuts off the flow of fluid through the conduit 227 and transmits pressurized hydraulic fluid through the conduit 225 by shifting the land 229 to the other side of conduit 191.

The phantom outline shows the cam follower 239 shifted to the trace 243.

In the misfire condition, the bolt 55 and injector 63 will remain locked in the forward position as illus trated. This mode of operation will be further described with reference to the cam traces shown in FIGS. 16 and 18 below.

The angle of the cam path 245 is such that the cam follower 239 will remain in the path 243 because of the direction of rotation of the cam 49. The valve spool 223 will thus remain in the rearward position illustrated by the phantom outline against the bias of the spring 235.

The conduits 211 and 213 extend from the bias control valve down to a bolt and injector system control valve indicated generally by the reference numeral 247.

The control valve 247 includes a valve housing 249. The valve housing 249 has a longitudinally extending central bore 251.

A compound spool is axially shiftable within the bore 251.

The compound spool includes an inner spool 253 and a sleeve 255. The sleeve 255 is axially shiftable on the reduced diameter central portion of the spool 253 between abuttment stops 257 and 259 at opposite ends of the spool 253.

The conduit 211 connects to the forward end of the housing 249 and the conduit 213 connects to the rearward end of the housing 249. When pressurized fluid is supplied through the conduit 211 as illustrated in FIG. 14B the sleeve 255 is shifted rearward and into engagement with the stop 259.

A cam follower 261 on the valve spool 253 rides in a trace 263 on the main cam 49. Rotation of the cam 49 periodically shifts the cam follower 261 forward to the position indicated by the dotted line to cause corre- 1 1 sponding shifting'of the valve spool 253 and the sleeve 2S5 engaged with stop 259.

Pressurized fluid is led into the control valve 247 by the conduit 227.

Conduits 262 and 265 extend from the valve housing 249 to the rear ends and to the front ends respectively of the actuators 83 and 68 for the bolt 55 and the yoke 61 of the propellant injection mechanism.

With the cam 49 in the position illustrated and the valve sleeve 255 pressed against the stop 259 of the spool 253, the pressurized fluid flows from the conduit 227 past a land 267 and to the conduit 262 and the back sides of the actuators 83 and 68. The respective pistons and the actuators are thus forced forward to the positions illustrated in FIG. 14B.

When the cam 49 rotates to a position in which the trace 263 shifts the cam follower 261 to the dotted line position shown in FIG. 1413 the land 267 closes off flow through the conduit 262 and directs the flow to the conduit 265 to reciprocate the pistons in the bolt actuator 83 and the propellant injection actuator 68 to the rear.

In this mode of operation the control valve 247 acts as an on-off valve or flow switching valve to cause reciprocation of the bolt and propellant injection mechanism with the movement of the cam follower 261. Conduits 269 and 271 extend downward from the valve housing 249 and connect with the return conduit 193. Flow through these conduits 269 and 271 is controlled by lands 273 and 275 on the valve sleeve 255. These lands open one side of each of the actuators 83 and 68 to hydraulic fluid return when the other side of each actuator is being pressurized.

Pressurized hydraulic fluid is supplied through the conduit 213 to shift the sleeve 255 forward against the stop 257 when the gun is placed in the armed condition (a condition in which the main cam drive motor is energized, the main cam is rotating and hydraulic power is applied to the gun module) and the trigger solenoid 197 is in the off position. In this condition of operation the reciprocation of the spool253 by the cam trace 263 is not effective to produce any reciprocation of the bolt and propellant injectors. Instead, pressurized hydraulic fluid is continuously transmitted from the conduit 227 to the conduit 265 past the land 267 and to the forward end of the actuators 83 and 68. The bolt and propellant injectors are thus held in the open position ready to start firing as soon as the trigger solenoid 197 is energized to the on position.

As illustrated in FIG. 14A the hydraulic drive control system includes a breech lock control valve indicated generally by the reference numeral 277 and a projectile loader control valve indicated generally by the reference numeral 279.

These control valves control the breech lock actuator 163 and the projectile loader actuator 112.

The control valves 277 and 279 are compound spool control valves like the bolt and injector control valve 247 and operate in a dual mode like the control valve 247.

Thus, a conduit 211 is connected to the forward end of a valve housing 281 of the control valve 277 and the conduit 211 is also connected to the forward end of a valve housing 283 of the control valve 279.

A conduit 213 is connected to the rearward end of the housing 281 and a rearward end of the housing 283. Pressurized hydraulic fluid is supplied to a central part 12 of each valve housing 281 and 283 by the conduit 227 during normal operation.

The pressurized fluid from the line 227 is directed alternately to the front and to the back side of the breech lock actuator 167 through conduits 285 and 287.

The breech lock control valve 277 includes a compound spool. The compound spool has an inner spool 289 and a valve sleeve 291. The valve sleeve 291 is shiftable on the spool 289 between the stops 293 and 295.

A land 297 controls the flow of fluid from conduit 227 to the conduits 285 and 287.

On a misfire, pressurized fluid from the main hydraulic line 191 is directed to the conduit 225 (see FIG. 14B), through an orifice 233, and, in the case of the breech lock actuator 163, through a conduit 299 and a one-way check valve 301 to the front end of the housing 167 to hold the breech lock in the locked position illustrated.

During normal cyclic firing operation pressurized hydraulic fluid is supplied to the front end of the housing 281 of the breech lock control valve to position the sleeve 291 against the stop 295 as illustrated in FIG. 14A.

A cam follower 303 on the valve spool 289 rides in a trace 305 on the cam 49. As the cam 49 rotates, the trace 305 periodically shifts the cam follower 303 to the forward position illustrated by the dotted outline. This in turn shifts the valve spool 289 and the valve sleeve 291 to produce reciprocation of the piston 169 in the breech lock actuator. Conduits 307 and 309 connect the valve housing 281 with the return line 193.

In the trigger off but armed condition pressurized hydraulic fluid is directed through the conduit 213 to the rear face of the sleeve 291 to move the sleeve forward against the stop 293. In this condition of operation, the breech lock actuator is maintained in the unlocked position ready for the start of firing. The reciprocation of the valve spool 295 by the cam follower 303 is not effective to change the flow of pressurized hydraulic fluid from the conduit 287 to the back side of the piston 169.

The conduit 227 includes a one-way check valve 311 and the conduit 309 includes a one-way check valve 313 for preventing bleed-off of pressure from the front part of the hydraulic actuator 167 during a misfire condition in which the breech lock is maintained in the locked position.

The projectile loader control valve 279 includes an inner valve spool 315 and a valve sleeve 317. The valve spool 315 has stops 319 and 321 at opposite ends of the valve spool. A cam follower 323 rides in a trace 325 on the cam 49 and is shiftable between the solid line position and the dotted line position shown to reciprocate the valve spool 315.

Pressurized hydraulic fluid supplied to the forward end of the valve housing by the conduit 211 during normal cyclic firing operation shifts the valve sleeve 317 rearward against stop 321 as illustrated.

Pressurized hydraulic fluid supplied through the conduit 213 to the rearward end of the valve housing 283 shifts the valve sleeve 317 forward against the stop 319 during the armed but non-firing condition of the gun.

Pressurized hydraulic fluid from the conduit 227 flows past a one-way check valve 327 and into the central part of the bore within the housing 283. From there the pressurized fluid flows either through a conduit 329 to the rearward end of the projectile loader actuator or through a conduit 331 to the forward end of the projec- 

1. A method of maintaining precise phase relationship between a control valve and a motor in a fluid-powered motor system, said control valve having a first cam follower and said motor having a second cam follower, and said method comprising, rotating a continuous cam, engaging the first cam follower of the control valve within two spaced-apart sides of a first cam trace of the cam to move the control valve back and forth as the cam rotates and to produce corresponding back and forth movement of the motor by directing pressurized fluid to opposite sides of the motor on each reciprocation of the control valve, and engaging the second cam follower of the motor within two spaced-apart sides of a second cam trace on the cam to interlock the movements of the control valve and motor through the cam and to insure that the control valve and the motor move in precise phase relationship with one another.
 2. A method as defined in claim 1 including arranging additional fluid-powered motor systems in adjacent relationship to said fluid-powered motor system and using common cam traces on said cam to control the corresponding control valves anD motors of each additional motor system.
 3. A fluid-powered actuator system comprising a control valve, an actuator motor, a source of high pressure fluid, and conduit means interconnecting the control valve and motor so that movement of the control valve back and forth directs high pressure fluid to opposite sides of the motor to produce corresponding back and forth movement of the actuator motor, a rotating cam, said control valve having a first cam follower, a first cam trace on the cam and having spaced-apart side surfaces engaging the first cam follower for maintaining the first cam follower between the side surfaces of said first cam trace and in a predetermined position on the cam at each angle of rotation of the cam, drive means for rotating the cam to produce movement of the control valve and corresponding movement of the actuator motor, said actuator motor having a second cam follower, and wherein said cam has a second cam trace having spaced-apart side surfaces engaging the second cam follower for maintaining the second cam follower between the side surfaces of said second cam trace and in a predetermined position on the cam at each angle of rotation of the cam, to interlock the movements of the control valve and actuator motor through the cam.
 4. A fluid-powered actuator system as defined in claim 3 wherein the cam is a cylindrical cam having a hollow interior configuration so that said actuator motor and a plurality of additional actuator motors can be arranged adjacent one another inside the cam and can be controlled in precise phase relationship with respect to one another by said cam and without imposing high face loadings on the cam.
 5. A fluid-powered actuator system as defined in claim 3 wherein the control valve has a valve body and first and second valve spools reciprocable within the valve body and to a limited extent with respect to one another, said valve body has a first port connected to one end of the actuator motor and a second port connected to the other end of the actuator motor and wherein the actuator system includes bias control valve means for shifting the first valve spool between a first position in which rotation of the cam and reciprocation of the second valve spool switches flow between the first and second ports and a second position in which rotation of the cam and reciprocation of the second valve spool does not switch flow from the first port. 